EP1965156B1 - Klimaanlage mit elektrischem Entspannungsventil - Google Patents

Klimaanlage mit elektrischem Entspannungsventil Download PDF

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Publication number
EP1965156B1
EP1965156B1 EP08100554.8A EP08100554A EP1965156B1 EP 1965156 B1 EP1965156 B1 EP 1965156B1 EP 08100554 A EP08100554 A EP 08100554A EP 1965156 B1 EP1965156 B1 EP 1965156B1
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EP
European Patent Office
Prior art keywords
temperature
compressor
fluid
condenser
expansion valve
Prior art date
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Not-in-force
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EP08100554.8A
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English (en)
French (fr)
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EP1965156A1 (de
Inventor
Jing Ming Liu
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Valeo Systemes Thermiques SAS
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Valeo Systemes Thermiques SAS
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Publication of EP1965156A1 publication Critical patent/EP1965156A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/17—Control issues by controlling the pressure of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the invention relates to air conditioning systems, in particular for motor vehicles.
  • An air conditioning installation of this type is equipped with an air conditioning circuit mainly comprising a compressor, a condenser or a gas cooler, an expansion device and an evaporator traversed, in this order, by a refrigerant.
  • the compressor compresses the refrigerant to bring it to a high pressure and then transmits it to the condenser, where it is cooled.
  • the refrigerant is expanded so as to lower its pressure.
  • the low pressure fluid then passes through the evaporator to be vaporized there before returning to the compressor.
  • An air flow passing through the evaporator is cooled or air conditioned and is sent to the passenger compartment of a motor vehicle.
  • air conditioning systems can also include an internal exchanger allowing heat to be exchanged between the refrigerant at two separate points in the air conditioning circuit.
  • Such installations are known in particular from documents EP-A-0 837 291 , EP-A-1 703 229 , JP 2002 081766 A or US 2007/000262 A .
  • the request of patent FR 2815 397 discloses an air conditioning installation comprising an internal exchanger whose efficiency is evaluated by means of temperature sensors, as well as by means of a refrigerant flow sensor.
  • the degree of opening is regulated by a control signal adapted as a function of certain operating parameters.
  • the known installations do not allow the degree of opening of the electric expansion valve to be optimized as a function of the operating conditions of the air conditioning and use a large number of sensors, thereby considerably increasing the overall cost of the installation.
  • such installations require the installation of sensors at different points, which has the consequence of making these installations more complex and bulky.
  • the invention aims to improve the situation by proposing an air conditioning installation, in particular for a motor vehicle, equipped with an air conditioning circuit according to claim 1.
  • the air conditioning installation is equipped with an air conditioning circuit comprising a compressor, a condenser, an electric expansion valve whose degree of opening varies according to a control signal, an evaporator, traversed in this order by a refrigerant, and an internal exchanger allowing the fluid circulating from the condenser to the expansion device to transfer heat to the fluid flowing from the evaporator to the compressor, the installation further comprising a control unit capable of controlling the control signal of the expansion valve on the basis of temperature and pressure measurements performed by a refrigerant pressure and temperature sensor placed at the outlet of the condenser and / or at the inlet of the expansion valve so as to regulate a control quantity relating to the sub-cooling of the condenser according to a chosen regulation law, the installation being characterized in that the control unit regulates the efficiency of the internal exchanger so as to guarantee protection against
  • the invention thus makes it possible to optimize the coefficient of performance (COP) of air conditioning while using a minimum number of sensors, and therefore to reduce the cost of the installation.
  • COP coefficient of performance
  • the invention further provides a method for regulating an air conditioning circuit as defined in claim 22.
  • FIG. 1 represents a diagram of an air conditioning circuit 10, intended in particular to be integrated in a motor vehicle.
  • the air conditioning circuit is traversed by a refrigerating fluid, in particular a fluoro-chlorinated fluid operating according to a subcritical cycle, such as for example the R-134a fluid.
  • a refrigerating fluid in particular a fluoro-chlorinated fluid operating according to a subcritical cycle, such as for example the R-134a fluid.
  • the present invention also covers the air conditioning circuits traversed by all alternative fluids used in thermodynamic loops for such installations and operating according to a super critical cycle.
  • the air conditioning circuit 10 mainly comprises a compressor 14, a condenser 11, an expansion device 12, and an evaporator 13, traversed in this order by the refrigerant.
  • the compressor 14 receives the fluid in the gaseous state and compresses it.
  • the high pressure refrigerant then passes through the condenser 11, where it is cooled.
  • the expansion device 12 then lowers the pressure of the fluid, before passing through the evaporator 13.
  • the fluid In the evaporator 13, the fluid is brought into the gaseous state so as to cool or air condition a flow of air passing through it. evaporator which can be sent to the passenger compartment of the vehicle.
  • the condenser 11 is traversed by an air flow making it possible to evacuate the heat taken from the refrigerant fluid.
  • the air flow passing through the condenser is, under certain operating conditions, set in motion by a motor-driven fan unit.
  • the refrigerant first undergoes desuperheating at constant pressure to lower the temperature of the fluid, then condensation at constant pressure.
  • the fluid is then sub-cooled in order to be able to supply the regulator with liquid.
  • the fluid in the liquid / vapor mixture state absorbs heat until all the liquid is vaporized.
  • the fully vaporized fluid is overheated.
  • the circuit also includes an internal heat exchanger 9, allowing the fluid flowing from the gas condenser 11 to the expansion device 12 to yield heat to the fluid flowing from the evaporator 13 to the compressor 14.
  • a bottle 18 can also be provided at the outlet of the condenser 11 to store the excess liquid which leaves therefrom.
  • the bottle 18 can be installed at the inlet of the expansion device 12.
  • the compressor 14 is in particular a compressor with external control and with variable displacement.
  • the invention can be applied to other types of compressors, for example compressors with internal clutch control, the invention is particularly advantageous for compressors with external control and with variable displacement. The following description will therefore be made with reference to a compressor 14 with external control and variable displacement, by way of nonlimiting example.
  • the expansion device 12 is an electric expansion valve.
  • the electrical expansion valves have a passage section, the degree of opening of which varies as a function of a control signal.
  • the figure 2 is a diagram showing a first alternative embodiment of an air conditioning installation 100 intended to equip a motor vehicle.
  • the installation is provided with the air conditioning circuit 10 described with reference to the figure 1 .
  • the installation comprises an air conditioning control device, not shown, for regulating the operating parameters of the air conditioning.
  • These parameters are in particular a function of the comfort conditions required by the user and defined by the indications carried by the control panel arranged in the passenger compartment of the vehicle. Likewise, these parameters are dependent on the external conditions and on the quantities measured on the air conditioning circuit.
  • the air conditioning control device includes an air conditioning computer to calculate some of the operating parameters, a unit for regulating the comfort of the air conditioning living space, and a cockpit control panel whose role is in particular to set the set point of the evaporation temperature T evapocons .
  • the installation comprises a control unit 40 adapted to control the control signal of the expansion valve 12 so as to regulate a control quantity relating to the overheating of the evaporator or the subcooling of the condenser 11 , according to a chosen regulatory law.
  • the control unit 40 proposed by the invention thus makes it possible to control the expansion valve 12 so as to optimize the overheating at the outlet of the evaporator or the sub-cooling at the inlet of the expansion valve 12.
  • the invention makes it possible not only to optimize the overheating at the outlet of the evaporator and the sub-cooling at the inlet of the expansion valve 12, but also to limit the temperature of the fluid at the inlet or at the outlet of the compressor.
  • the invention thus makes it possible to limit the setpoint for overheating and / or subcooling by taking into account the maximum imbalance between the temperatures of the evaporator. This imbalance is in fact known to have a great influence on the comfort of the user. By indirectly controlling this imbalance, the invention consequently improves comfort in the passenger compartment while optimizing the coefficient of performance (COP) of the air conditioning circuit.
  • COP coefficient of performance
  • the figures 2 and 3 correspond to a first embodiment in which the operation of the expansion valve 12 is controlled by the control unit 40 so as to regulate a quantity relating to the overheating of the evaporator, according to a chosen regulation law.
  • the quantity relating to the overheating of the evaporator corresponds in particular to the difference between two measured temperature measurements representative of the overheating of the evaporator 13.
  • the quantity relating to overheating corresponds to the difference (T out - T in ) between the temperature T out of the refrigerant at the outlet of the evaporator and the temperature T in of the refrigerant at the inlet of the evaporator.
  • the temperatures T out and T in are, according to the embodiment of the figure 2 , measured using 24 and 22 temperature probes placed respectively at the outlet of the evaporator and at the inlet of the evaporator, in contact with the refrigerant.
  • the quantity relating to the evaporator overheating corresponds to the difference (T max -T min ) between the maximum temperature T max of the evaporator 13 and the minimum temperature T min of the evaporator 13 of the air passing through the evaporator 13, at the overheating zone.
  • the temperatures T max and T min are, according to the embodiment of the figure 3 , be measured using thermistor probes of conventional structure 23 and 21 placed in the fins of the evaporator 13 or behind the evaporator 13 respectively in the "warmest” zone and the "coldest” zone of the evaporator 13, in its overheating zone.
  • the location of the temperature probes is determined by the map of the evaporator 13, that is to say the temperature distribution of the evaporator 13.
  • warmest zone is meant the region of the evaporator 13 having the highest temperature and by “coldest” zone is meant the region of the evaporator 13 having the lowest temperature.
  • the variant of the figure 3 makes it possible to measure the imbalance of the temperature of the air flow passing through the evaporator, without having to insert two temperature sensors in the conduits of the air conditioning circuit, and therefore makes it possible to limit fluid leaks.
  • control unit 40 regulates the operation of the expansion valve 12 by controlling the quantity relating to overheating, that is to say ( T out -T in ) in the case of figure 2 or (T max - T min ) in the case of figure 3 , according to an adapted regulatory law.
  • the regulation law can be closed loop regulation, for example of PID (Proportional Integral Derivative) type.
  • the control unit determines the setpoint of the quantity relating to overheating, namely (T out - T in ) cons or (T max - T min ) cons as appropriate, then compares the quantity relating to the overheating, as determined from the measurements provided by the sensors 24 and 22, or 23 and 21, as the case may be, at the setpoint of this quantity.
  • the control signal of the expansion valve 12 is then adjusted as long as the quantity relating to overheating has not reached its setpoint.
  • the invention proposes to regulate the compressor 14, when the latter is an externally controlled compressor.
  • An externally controlled compressor is fitted with a control valve which adjusts the displacement of the compressor according to a control signal.
  • Compressors with external control are conventionally controlled using a closed loop regulation law, for example a PID type regulation, which is based on minimizing the difference between the measurement of the evaporation temperature T evapo of the compressor and the setpoint T evapocons of the compressor evaporation temperature (T evapo - T evapocons ).
  • the temperature set point evaporation represents the target temperature requested in the passenger compartment by a passenger in the vehicle.
  • the invention provides for implementing such a law for regulating the compressor with external control 14 by using the temperature measurements which involve the control variable relating to overheating, that is to say T in and T out in the case of the figure 2 or T min and T max in the case of figure 3 , to calculate the value of the evaporation temperature, to be regulated according to the chosen compressor regulation law.
  • x is a coefficient obtained experimentally or calculated to estimate the temperature of the air passing through the evaporator.
  • x is a coefficient obtained experimentally or calculated to estimate the temperature of the air passing through the evaporator.
  • the value of the evaporation temperature obtained in accordance with the variant of the figure 3 represents the average air temperature behind the evaporator.
  • the control unit 40 can then implement conventional regulation, for example of the PID type, of the compressor so as to minimize the difference between the value thus calculated of the evaporation temperature T evapo and the temperature set point of evaporation T evapocons , supplied by the cockpit control panel.
  • FIG. 4 illustrates the control of the expansion valve 12 and the externally controlled compressor according to the variant of the figure 2 .
  • This block diagram applies analogously to the embodiment of the figure 3 , replacing the parameter T in with T min and the parameter T out with T max .
  • step 300 the control unit 40 determines the setpoint of the quantity relating to overheating (T out - T in ) cons .
  • This setpoint will be determined according to the curve giving the relationship between the overheating and the optimal coefficient of performance (COP).
  • COP coefficient of performance
  • step 301 the control unit 40 then determines the quantity relating to overheating (T out -T in ) from measurements of the temperatures T out and T in .
  • step 302 the control unit then compares the quantity relating to the overheating determined in step 301 to its setpoint obtained in step 300.
  • the control signal of the expansion valve 12 is then adjusted as long as the quantity relating to the overheating has not reached its setpoint, in step 302 (PID regulation).
  • control unit 40 controls the compressor 14 so as to regulate the evaporation temperature T evapo .
  • step 310 the control unit 40 determines the evaporation temperature from the temperature measurements T out and T in .
  • step 312 the control unit then compares the value of the evaporation temperature T evapo obtained in step 310 with its setpoint T evapocons , supplied by the cockpit control panel.
  • the control signal of the compressor 14 is then adjusted as long as the quantity relating to the overheating has not reached its setpoint, in step 312 (PID regulation).
  • control unit 40 can additionally use the values of the parameters for discharging the coolant leaving the compressor 14 to control the expansion valve 12 and, where appropriate, the compressor 14.
  • the installation provides for this a temperature and pressure sensor 20 placed at the outlet of the compressor 14 or at the inlet of the condenser 11 to measure the discharge pressure Pr and the discharge temperature Tr of the refrigerant at the inlet of the condenser.
  • the values of these parameters Pr and Tr supplied by the sensor 20 are then compared with threshold values, and depending on the result of this comparison, the operation of the expansion valve 12 and, if necessary, that of the compressor 14 are adapted.
  • control unit increases the opening of the expansion valve 12, if it is determined that the values measured by the sensor 20 are greater than their respective thresholds, and decreases the capacity of the compressor 14 if the degree of opening of the expansion valve 12 is greater than a predetermined opening threshold, which makes it possible to maintain the discharge parameters Pr and Tr at an acceptable level.
  • the first embodiment uses only three sensors to control the expansion valve 12 and, if necessary, the compressor 14.
  • the installation does not use a pressure sensor at the outlet of the evaporator 13 to control the expansion valve 12 and the compressor 14, which makes it possible to reduce the costs of the installation.
  • control unit 40 controls the control signal of the expansion valve 12 so as to regulate a control quantity relating to the sub-cooling at the inlet of the expansion valve 12, according to a law of the chosen regulation.
  • the regulation of the sub-cooling at the inlet of the expansion valve 12 makes it possible to act indirectly on the overheating at the outlet of the evaporator 13.
  • control unit regulates the temperature Tsc of the refrigerant, as a quantity relating to subcooling.
  • the sub-cooling temperature Tsc of the refrigerant corresponds to the temperature of the refrigerant at the inlet of the expansion valve 12.
  • This temperature can be measured using a temperature probe 29 placed at the inlet of the expansion valve 12.
  • the control unit 40 controls the expansion valve 12 so as to regulate the temperature Tsc according to a chosen regulation law, for example a closed-loop regulation law of the PID type. For this, the control unit 40 determines the setpoint of the fluid temperature at the inlet of the expansion valve 12, Tsc cons , then controls the opening of the expansion valve 12 so as to reduce the difference between the measurement of the temperature Tsc supplied by the sensors 29 and the setpoint of the temperature Tsc cons . Tsc cons is determined according to a relationship between subcooling and the optimal coefficient of performance (COP). Control of Tsc cons is simple.
  • a temperature and pressure sensor 20 can be used in addition to the output of the compressor 14, in a similar manner to the first embodiment.
  • the temperature Tsc of sub-cooling of the refrigerant corresponds to the temperature of the refrigerant at the outlet of the condenser 11. This temperature can be measured using a temperature probe 26 placed at the outlet of the condenser 11.
  • the control unit 40 manages the expansion valve 12 so as to regulate the pressure measured by the sensor 20 so that the pressure is correlated with the determined law, for example a closed-loop regulation law of the PID type, for the temperature measured by the sensor 26.
  • FIGS. 7 and 8 represent variants according to the invention of the second embodiment in which the control unit 40 further controls the performance of the internal exchanger so as to limit the suction and discharge temperature of the compressor 14, or in which the control unit 40 controls the performance of the internal exchanger from the mass flow rate Mc of the refrigerant, in addition to the regulation of the control quantity relating to subcooling.
  • control unit 40 controls the expansion valve 12 so as to regulate the high pressure of the HP refrigerant, according to a chosen regulating law.
  • control unit 40 controls the efficiency E IHX of the internal exchanger 9 to further adjust the operation of the expansion valve 12.
  • the control unit 40 performs the regulation of the high pressure HP by comparing a measurement of the high pressure HP with its reference value HP cons , according to the chosen regulation law, for example a closed loop regulation law, of the type PID, and acts on the expansion valve 12 according to the result of this comparison.
  • the chosen regulation law for example a closed loop regulation law, of the type PID
  • the measurement of the high pressure HP is obtained by means of a sensor 27 placed at the outlet of the condenser 11 which supplies the pressure of the refrigerant fluid at the outlet of the condenser 11. Furthermore, the control unit 40 calculates the high pressure setpoint HP cons from the measurement of the temperature Tsc of the refrigerant at the outlet of the condenser. In this variant, it is advantageous to also measure the temperature Tsc at the outlet of the condenser 11 since this makes it possible to use a single temperature and pressure sensor 27, placed at the outlet of the condenser 11, which provides both the temperature Tsc and the HP pressure of the refrigerant.
  • the control unit 40 regulates the sub-cooling SC by comparing a calculated value of the sub-cooling SC with its set value SC cons , according to the chosen control law, for example a closed-loop control law, of the PID type. . It then acts on the expansion valve 12 according to the result of this comparison.
  • the chosen control law for example a closed-loop control law, of the PID type.
  • the value of the sub-cooling SC is obtained by virtue of a sensor 27 placed at the outlet of the condenser 11 which provides a measurement of the temperature Tsc of sub-cooling of the coolant and a measurement of the high pressure HP of the coolant at the inlet of the valve. expansion 12.
  • the measurement of the high pressure makes it possible to determine the saturation temperature Tsat of the refrigerant.
  • control unit 40 additionally regulates the efficiency E IHX of the internal exchanger 9 by comparing it to an efficiency limit L IHX .
  • the operation of the control valve is adjusted when the result of the comparison indicates that the efficiency E IHX exceeds the efficiency limit L IHX .
  • the efficiency E IHX of the internal exchanger 9 to control the expansion valve 12 makes it possible to guarantee protection against an excessively high discharge temperature of the compressor and to limit the pressure compressor suction.
  • the efficiency of the internal exchanger 9 is estimated from the flow rate of the refrigerant.
  • the mass flow Mc can be calculated from the condenser model, therefore from the sub-cooling temperature Tsc, the ambient temperature and the high pressure HP, a measurement of which is provided by the sensor 27.
  • control unit 40 manages the expansion valve 12 so as to regulate the sub-cooling of the refrigerant and the efficiency of the internal exchanger 9 in order to limit the suction and discharge temperature of the compressor 14.
  • the control unit 40 can estimate the efficiency E IHX of the internal exchanger 9 by calculating the mass flow rate of refrigerant fluid Mc.
  • the value of the efficiency E IHX of the internal exchanger 9 can then be estimated experimentally or by simulations, from the calculated value of the mass flow rate of refrigerant Mc. For example, it can be determined using a diagram similar to that of the figure 11 .
  • the figure 11 indeed gives an example of an evolution law linking the efficiency E IHX of the internal exchanger to the fluid flow rate Mc. It shows in particular that the efficiency E IHX decreases as a function of the fluid flow rate Mc and that to a given value Mc (0) corresponds a unique value E IHX (0) on the curve.
  • the control unit 40 can therefore derive an estimate of the efficiency of the internal exchanger E IHX from such a diagram, from the calculated value of the flow rate of refrigerant fluid M C.
  • the figure 9 represents a simplified variant of the figure 8 , in which the air conditioning circuit is not provided with an internal exchanger. This variant is therefore not in accordance with the invention.
  • a dehydrating tank 16 can be provided at the outlet of the condenser 11 to ensure a reserve of cooling fluid, supply the regulator with liquid, and / or eliminate harmful acids and foreign particles.
  • a temperature and pressure sensor 30 at the outlet of the condenser 11 is provided for regulating the sub-cooling SC or regulating the pressure HP as described with reference to figures 7 or 8 .
  • this variant only involves two sensors: a temperature and pressure sensor 30 used to control the expansion valve 12, and a temperature probe 25 used to control the compressor 14.
  • step 322 the control unit 40 determines the setpoint of the quantity HP relating to the subcooling HP cons , from the measurement of the temperature Tsc supplied by the sensor 27 in step 320.
  • step 324 the control unit 40 receives the measurement of the quantity HP from the sensor 27.
  • step 326 the control unit then compares this HP measurement with its HP cons setpoint obtained in step 322.
  • step 326 PID regulation
  • the control signal from the expansion valve 12 is then adjusted as long as the HP quantity has not reached its setpoint.
  • control unit 40 controls the efficiency E IHX of the internal exchanger 9, in step 330, by comparing it to an efficiency limit L IHX .
  • control unit 40 estimates beforehand the fluid flow rate Mc by the condenser model, the efficiency E IHX from the estimated fluid flow rate Mc, and determines the efficiency limit L IHX . Operation of the control valve is adjusted when the result of the comparison indicates that the efficiency E IHX exceeds the efficiency limit L IHX .
  • control unit 40 controls the compressor 14 so as to regulate the evaporation temperature T evapo : the control unit 40 compares, in step 350, the value of the evaporation temperature T evapo with its T evapocons setpoint, provided by the cockpit control panel. The control signal of the compressor 14 is then adjusted as long as the quantity relating to the overheating has not reached its setpoint.
  • the functional diagram of the figure 12 illustrates the control of the expansion valve 12 and the externally controlled compressor according to the variant of the figure 8 .
  • step 340 the control unit 40 determines the subcooling setpoint SC cons according to a table established by test or simulation results. SC cons corresponds to the maximum of the optimal coefficient of performance (COP).
  • control unit 40 then calculates the value of the sub-cooling SC from the measurement of the high pressure HP and the measurement of the temperature Tsc, at the input of the expansion valve 12, supplied by the sensor 28.
  • step 344 the control unit then compares this value SC with its instruction SC cons .
  • the control signal of the expansion valve 12 is then adjusted as long as the quantity relating to overheating has not reached its setpoint.
  • the control unit 40 can additionally control the efficiency E IHX of the internal exchanger 9 and the compressor 14, as described with reference to figure 7 .
  • the invention therefore makes it possible to control the electric expansion valve 12 and, where appropriate, the externally controlled compressor 14 by optimizing the coefficient of performance (COP) and by using a minimum number of sensors in the air conditioning circuit.
  • the invention makes it possible to avoid the use of a pressure sensor at the outlet of the evaporator and thus to reduce the costs of the installation.
  • the installations described comprise internal exchangers.
  • the examples described were made by taking circuits incorporating a condenser.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Air Conditioning Control Device (AREA)

Claims (22)

  1. Klimaanlage, insbesondere für ein Kraftfahrzeug, mit einem Klimatisierungskreislauf, umfassend einen Kompressor (14), einen Kondensator (11), ein elektrisches Entspannungsventil (12), dessen Öffnungsgrad in Abhängigkeit von einem Stellsignal variiert, einen Verdampfer (13), die in dieser Reihenfolge von einem Kältemittel durchflossen werden, und einen internen Tauscher (9), der es dem vom Kondensator (11) zur Entspannungsvorrichtung (12) zirkulierenden Mittel ermöglicht, Wärme an das vom Verdampfer (13) zum Kompressor (14) zirkulierende Mittel abzugeben, wobei die Klimaanlage ferner eine Steuerungseinheit (40) umfasst, die geeignet ist, das Stellsignal des Entspannungsventils (12) ausgehend von Temperatur- und Druckmessungen, die von einem Sensor für Druck und Temperatur des Kältemittels (27, 28) durchgeführt werden, der am Auslass des Kondensators und/oder am Einlass des Entspannungsventils (12) angeordnet ist, zu steuern, so dass eine Stellgröße bezüglich der Unterkühlung des Kondensators (11) nach einem ausgewählten Regelungsgesetz geregelt wird, wobei die Anlage dadurch gekennzeichnet ist, dass sie über das Stellsignal des Entspannungsventils (12) den Wirkungsgrad des internen Tauschers (9) regelt, so dass ein Schutz vor einer zu hohen Austrittstemperatur garantiert wird und der Ansaugdruck des Kompressors begrenzt wird, wobei die Steuerungseinheit (40) geeignet ist, den Wirkungsgrad des internen Tauschers mit einem vorgegebenen Schwellenwert zu vergleichen, um den Wirkungsgrad des internen Tauschers (9) zu regeln, wobei die Steuerungseinheit (40) auch geeignet ist, den Wert des Wirkungsgrads des internen Tauschers (9) ausgehend vom Massenstrom des Kältemittels zu bestimmen, der in Abhängigkeit von Messungen des hohen Drucks und der Unterkühlungstemperatur des Kältemittels geschätzt wird.
  2. Anlage nach Anspruch 1, dadurch gekennzeichnet, dass die Steuerungseinheit (40) geeignet ist, die Regelung der Stellgröße durchzuführen, indem sie die Stellgröße mit einem Sollwert der Stellgröße vergleicht.
  3. Anlage nach Anspruch 2, dadurch gekennzeichnet, dass die auf die Überhitzung bezogene Größe der Differenz zwischen zwei Temperaturmessungen entspricht, die jeweils der am Einlass und am Auslass des Verdampfers (13) abgegriffenen Temperatur des Mittels entsprechen.
  4. Anlage nach Anspruch 3, dadurch gekennzeichnet, dass sie zwei Temperaturfühler (22, 24) umfasst, die in Kontakt mit dem Mittel im Einlass und im Auslass des Verdampfers angeordnet sind und geeignet sind, die beiden Temperaturmessungen abzugeben.
  5. Anlage nach Anspruch 2, dadurch gekennzeichnet, dass die auf die Überhitzung bezogene Größe der Differenz zwischen zwei Temperaturmessungen entspricht, die jeweils der höchsten Temperatur und der niedrigsten Temperatur des den Verdampfer (13) überstreichenden Luftstroms entsprechen.
  6. Anlage nach Anspruch 5, dadurch gekennzeichnet, dass sie zwei Temperaturfühler (21, 23) umfasst, die in den Rippen des Verdampfers (13) und/oder hinter dem Verdampfer (13) angeordnet sind und geeignet sind, jeweils eine Messung der höchsten Temperatur und der niedrigsten Temperatur abzugeben.
  7. Anlage nach einem der Ansprüche 2 bis 6, dadurch gekennzeichnet, dass der Kompressor (14) ein Kompressor mit externer Steuerung ist, der mit einem Steuerventil versehen ist, dessen Durchlassquerschnitt in Abhängigkeit von einem Stellsignal variiert, und dass die Steuerungseinheit (40) geeignet ist, das Stellsignal des Kompressors (14) so zu steuern, dass die Verdampfungstemperatur des Verdampfers (13) geregelt wird und/oder die Austritts- oder Ansaugtemperatur des Kompressors (14) begrenzt wird, wobei die Verdampfungstemperatur in Abhängigkeit von den Temperaturmessungen berechnet wird.
  8. Anlage nach Anspruch 2, dadurch gekennzeichnet, dass die auf die Unterkühlung bezogene Größe der Unterkühlungstemperatur des Kältemittels entspricht.
  9. Anlage nach Anspruch 8, dadurch gekennzeichnet, dass sie einen Temperaturfühler (26) umfasst, der in Kontakt mit dem Mittel im Auslass des Kondensators (11) angeordnet ist.
  10. Anlage nach Anspruch 8, dadurch gekennzeichnet, dass sie einen Temperaturfühler (29) umfasst, der in Kontakt mit dem Mittel im Einlass des Entspannungsventils (12) angeordnet ist und geeignet ist, eine Messung der Unterkühlungstemperatur abzugeben.
  11. Anlage nach einem der Ansprüche 8 bis 10, dadurch gekennzeichnet, dass der Kompressor (14) ein Kompressor mit externer Steuerung ist, der mit einem Steuerventil versehen ist, dessen Durchlassquerschnitt in Abhängigkeit von einem Stellsignal variiert, und dass die Steuerungseinheit (40) ferner geeignet ist, das Entspannungsventil und den Kompressor so zu steuern, dass die Austrittstemperatur und der Austrittsdruck im Auslass des Kompressors (14) unter jeweiligen vorbestimmten Schwellenwerten gehalten werden.
  12. Anlage nach Anspruch 2, dadurch gekennzeichnet, dass die auf die Unterkühlung bezogene Größe der Differenz zwischen der Sättigungstemperatur des Kältemittels und der Unterkühlungstemperatur des Kältemittels entspricht.
  13. Anlage nach Anspruch 12, dadurch gekennzeichnet, dass sie einen Temperatursensor (28) umfasst, der in Kontakt mit dem Mittel im Einlass des Entspannungsventils (12) angeordnet ist und geeignet ist, eine Messung der Unterkühlungstemperatur abzugeben.
  14. Anlage nach einem der Ansprüche 12 und 13, dadurch gekennzeichnet, dass sie einen Drucksensor (28) umfasst, der in Kontakt mit dem Mittel im Einlass des Entspannungsventils (12) angeordnet ist und geeignet ist, eine Messung des Drucks im Einlass des Entspannungsventils (12) abzugeben, und dass die Steuerungseinheit (40) geeignet ist, die Sättigungstemperatur des Mittels ausgehend von der Druckmessung zu schätzen.
  15. Anlage nach Anspruch 2, dadurch gekennzeichnet, dass die auf die Unterkühlung bezogene Größe dem Druck und der Temperatur im Auslass des Kondensators (11) entspricht.
  16. Anlage nach Anspruch 15, dadurch gekennzeichnet, dass sie einen Drucksensor (27) im Auslass des Kondensators umfasst, um den Druck des Mittels im Auslass des Kondensators (11) zu messen.
  17. Anlage nach einem der Ansprüche 15 und 16, dadurch gekennzeichnet, dass sie einen Temperatursensor (27) umfasst, der geeignet ist, eine Messung der Temperatur des Mittels im Auslass des Kondensators (11) abzugeben, und dass die Steuerungseinheit geeignet ist, den Sollwert des Drucks im Auslass des Kondensators ausgehend von der vom Sensor abgegebenen Temperaturmessung zu schätzen.
  18. Anlage nach Anspruch 17, dadurch gekennzeichnet, dass der Temperatursensor (27) in Kontakt mit dem Mittel im Auslass des Kondensators (11) angeordnet ist.
  19. Anlage nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie einen Temperatur- und Drucksensor (27) umfasst, der im Auslass des Kondensators angeordnet ist, um den hohen Druck und die Unterkühlungstemperatur des Kältemittels zu messen.
  20. Anlage nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Regelung der Stellgröße eine Regelung im geschlossenen Regelkreis ist.
  21. Anlage nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Steuerungseinheit (40) das Stellsignal des Entspannungsventils und/oder des Kompressors verwaltet, um die Auslass- und/oder Ansaugtemperatur des Kompressors zu begrenzen.
  22. Verfahren zur Regelung eines Klimatisierungskreislaufs, umfassend einen Kompressor (14), einen Kondensator (11), ein elektrisches Entspannungsventil (12), dessen Öffnungsgrad in Abhängigkeit von einem Stellsignal variiert, und einen Verdampfer (13), die in dieser Reihenfolge von einem Kältemittel durchflossen werden, und einen internen Tauscher (9), der es dem vom Kondensator (11) zur Entspannungsvorrichtung (12) zirkulierenden Mittel ermöglicht, Wärme an das vom Verdampfer (13) zum Kompressor (14) zirkulierende Mittel abzugeben,
    wobei bei dem Verfahren das Stellsignal des Entspannungsventils (12) ausgehend von Temperatur- und Druckmessungen gesteuert wird, die von einem Sensor für Druck und Temperatur des Kältemittels (27, 28) durchgeführt werden, der im Auslass des Kondensators (11) und/oder im Einlass des Entspannungsventils (12) angeordnet ist, so dass eine Stellgröße bezüglich der Unterkühlung des Kondensators (11) nach einem ausgewählten Regelungsgesetz geregelt wird,
    wobei das Verfahren gekennzeichnet ist durch die Regelung des Wirkungsgrades des internen Tauschers (9) über das Stellsignal des Entspannungsventils (12), so dass ein Schutz vor einer zu hohen Austrittstemperatur des Kompressors garantiert wird und der Ansaugdruck des Kompressors begrenzt wird, wobei die Steuerung den Wirkungsgrad des internen Tauschers (9) mit einem vorgegebenen Schwellenwert vergleicht, um den Wirkungsgrad des internen Tauschers (9) zu regeln, und den Wert des Wirkungsgrades des internen Tauschers (9) ausgehend vom Massenstrom des Kältemittels bestimmt, der in Abhängigkeit von Messungen des hohen Drucks und der Unterkühlungstemperatur des Kältemittels geschätzt wird.
EP08100554.8A 2007-02-28 2008-01-16 Klimaanlage mit elektrischem Entspannungsventil Not-in-force EP1965156B1 (de)

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JP2008213830A (ja) 2008-09-18
US20080229770A1 (en) 2008-09-25
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FR2913102A1 (fr) 2008-08-29
EP1965156A1 (de) 2008-09-03
JP5543689B2 (ja) 2014-07-09

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